CN105324564A - Method and device for operating a gas internal combustion engine - Google Patents

Method and device for operating a gas internal combustion engine Download PDF

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Publication number
CN105324564A
CN105324564A CN201480019065.9A CN201480019065A CN105324564A CN 105324564 A CN105324564 A CN 105324564A CN 201480019065 A CN201480019065 A CN 201480019065A CN 105324564 A CN105324564 A CN 105324564A
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CN
China
Prior art keywords
mixture
gas
share
pumping stages
volume
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Granted
Application number
CN201480019065.9A
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Chinese (zh)
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CN105324564B (en
Inventor
A.弗洛尔
A.格勒
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Rolls Royce Solutions Ltd.
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MTU Motoren und Turbinen Union Muenchen GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/04—Gas-air mixing apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0418—Layout of the intake air cooling or coolant circuit the intake air cooler having a bypass or multiple flow paths within the heat exchanger to vary the effective heat transfer surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/16—Control of the pumps by bypassing charging air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
    • F02D19/021—Control of components of the fuel supply system
    • F02D19/023—Control of components of the fuel supply system to adjust the fuel mass or volume flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
    • F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
    • F02D19/10—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous
    • F02D19/105—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous operating in a special mode, e.g. in a liquid fuel only mode for starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0027—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures the fuel being gaseous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/04—Gas-air mixing apparatus
    • F02M21/047—Venturi mixer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
    • F02D2041/1433—Introducing closed-loop corrections characterised by the control or regulation method using a model or simulation of the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
    • F02D2041/1433—Introducing closed-loop corrections characterised by the control or regulation method using a model or simulation of the system
    • F02D2041/1434—Inverse model
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/04—Engine intake system parameters
    • F02D2200/0402—Engine intake system parameters the parameter being determined by using a model of the engine intake or its components
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • General Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)

Abstract

The invention relates to a method for operating a gas internal combustion engine (100). The gas internal combustion engine has a gas mixer (40), an intake section (30) and an engine (10) with a number of cylinders, wherein in the method, a fuel mixture comprising a charging mixture is fed to the engine (10), and the engine (10) is operated in the gas mode with gas as the fuel in the charging mixture, wherein by means of an input mixture portion, assigned to at least one earlier mixture state, of a gas/air mixture, an output mixture portion, assigned to a later mixture state, of the gas/air mixture is determined, and wherein the determination is carried out by means of an intake section model which serves as a basis of a computing model for the intake section (30). The invention provides that the output mixture portion of the gas/air mixture is determined at an engine feed; and the input mixture portion of the output mixture portion is determined over a number of intermediate states of the mixture portion in a number of assigned volumes of the intake section (30), wherein the intake mixture portion of a gas/air mixture is determined at the gas mixer (40), and an air stream and/or gas stream is set at the gas mixer (40) in accordance with the input mixture portion.

Description

For the method and apparatus of operating gas internal-combustion engine
Technical field
The present invention relates to a kind of method for operating gas internal-combustion engine, this gas internal-combustion engine has fuel gas mixer, pumping stages (Ansaugstrecke) and the motor with multiple cylinder.The present invention relates to a kind of adjusting portion for internal-combustion engine as described in the preamble according to claim 13 and a kind of internal-combustion engine as described in the preamble according to claim 14 in addition.Gas internal-combustion engine has plenum and the bypass section for walking around plenum in addition in pumping stages.Gas internal-combustion engine is the gas internal-combustion engine of especially spark ignition.
Background technique
The application of the gas internal-combustion engine of the type be Mobile solution (such as in navigation field or in commercial car and heavy vehicle field) and static application as in monoblock power station, it especially advantageously will be designed for the gas supply of fluctuation.
File 6,131,552 always disclose a kind of Fuel Control System, and it can be adjusted to the fuel gas supply of mixing chamber according to the engine operating state recorded.File US6, the controlling method of 131,552A or other only relevant to load combustion gas dispensing also turn out to be inadequate in the regulating system of complexity.
Usually, air consumption is the tolerance being fed to the gaseous state fresh charge of internal-combustion engine to pressurized air in charge mixture (Ladegemisch), and wherein, air consumption also allows the quality that gas handling system and intake process are described.Usually, actual air consumption represents the ratio of fresh air quantity in charge mixture being actually delivered to motor or its cylinder during work cycle.The mixture quality of this reality, relative to fresh charge quality (motor for free air-breathing) or stoichiometric charge density measurement in the motor of supercharging by the discharge capacity of geometry with in ambient condition of theory, considers the state of the fresh charge after the compressor or after compressed air cooler at this.
Series of factors impact flows to the fresh charge of cylinder, the opening cross-section of such as valve or valve control time.In principle, it can be determined by the module for determining engine booster, and pumping stages model is stored in this module.But the fresh charge in fact, flowing to motor in charge mixture only in special circumstances corresponding to theoretical value.Air consumption is not the number for constant engine, but depends on the current geometry situation of rotating speed and air inlet system and firing chamber to a great extent; In order to grasp this relation, such as, can consider suitable characteristic field.
Such as by file EP1398490A2, known pumping stages model in the engine controller substantially in common internal-combustion engine.What they were common is, when setting up pumping stages model, (in the simplest situation as uniform pressurized container to obtain dynamic process in air path) is as basic thought widely, by fill and purging method designs the storage characteristics of pumping stages (also referred to as pumping tube).At this, pumping tube processes as pressurized container, its filled with air continuously by throttle valve and motor by its suction properties corresponding to working stroke by suction valve from wherein withdrawing air.
But demonstrate, especially in the transient working scope of internal-combustion engine and when variable fuel mass, the fuel supply of gas internal-combustion engine is also more complex.Especially demonstrate in gas internal-combustion engine, especially in order to construct the gas internal-combustion engine of spark ignition, the operation in low loading range and/or in transient load scope may have problem.
When gas engine is run, mixture is formed and usually carried out before the compressor of exhaust gas turbocharge.Meanwhile, the pumping stages between compressor outlet and firing chamber import comprises the large volume of part, and it stores thus or sends significant mixture quality.If cause the pressure in each subvolumes and/or temperature variation when load and/or the rotation speed change of motor, so this is especially applicable.Due in gas internal-combustion engine but (because especially coarse due to the large volume of the part) mixture quality only matched with operating point is conditionally formed, the discharge (NOx, CO, particle etc.) that can expect high hydrocarbon emission (HC discharge) or other raising and the poor efficiency caused by unburnt combustion gas.
It is desirable that, in transient operation, the combustion gas operation of gas internal-combustion engine is especially more advantageously designed corresponding to load request and conditions of discharge.Especially in low loading range, at least realize this is be worth expecting.Especially in full-load range, that is preferably until 100% ground realize this be worth expect.
Summary of the invention
Thus, the present invention its objective is and a kind of method and apparatus is described, realizes the operation as the internal-combustion engine of the improvement of gas internal-combustion engine by means of it.Object of the present invention especially realizes the improvement in transient operation and/or the improvement in discharge field.Preferably, the propellant composition problem existed in low loading range should be realized in an improved way, when especially avoiding the moment of torsion sudden change of motor in other transient operation, also when load request changes and as far as possible when avoiding excess emissions.Especially as far as possible advantageously should design mixture quality to be formed.Especially should the air consumption of designed engines in an improved way.At least one during object of the present invention especially solves the problem.At least alternative solution should be proposed.
The object relating to method is realized by one method according to claim 1 by the present invention.
Set out in the method for operating gas internal-combustion engine of this type mentioned especially from the outset, this gas internal-combustion engine has fuel gas mixer, pumping stages and the motor with multiple cylinder, wherein, in the method
-fuel mixture is comprised charge mixture flow to motor and utilize in charge mixture as the combustion gas of fuel to run motor in combustion gas runs.
In addition be arranged to, by means of the input be associated with the mixture state before at least one-mixture share of air-gas mixture to determine the output be associated with the mixture state afterwards-mixture share of air-gas mixture, and wherein, this determines the pumping stages model realization on the basis by means of the computation model being used as pumping stages.
One-tenth arranged according to the present invention, determine the output-mixture share of the air-gas mixture at motor supply unit place, and in multiple volumes be associated of pumping stages by multiple intermediatenesses of mixture share by exporting-mixture share determines input-mixture share.To this, determine the air-gas mixture at fuel gas mixer place input-mixture share and according to the input-mixture share air stream of adjustment at fuel gas mixer place and/or gas flow.Advantageously, can in the scope of real-time calculating at the same time at fuel gas mixer place according to input-mixture share, especially mixture quality stream adjustment air stream and/or gas flow.
The present invention is from this idea, namely should as far as possible when considering the state pressure of pumping stages, especially when considering the throttling of pressurized air or fuel mixture and/or carry out the favourable transient operation of gas internal-combustion engine when considering air consumption as far as possible better, wherein, the feature of gas engine be considered.Although the pumping stages model in engine controller is known substantially.But the present invention is from this idea, namely just for the application of the gas engine of the mixture formation especially had before compressor, the modeling mentioned by beginning is substantially not enough.
First the present invention considers this idea, namely in gas engine in the place that mixture is formed, section such as before the compressor in exhaust gas turbocharge portion and between the position of entry of combustion chamber can be relative long and itself comprise larger volume thus, its almost can not be realistic in the state of static state describe.First the present invention also considers, pumping stages in gas engine between compressor outlet and entry of combustion chamber is made up of the larger volume of part (when the pressure caused when the load of motor and/or rotation speed change in each subvolumes and/or temperature variation, these storage volumetric or send significant mixture quality).
The present invention recognizes, therefore special in gas engine the mixture quality stream in the outlet port of fuel gas mixer temporarily with the decoupling at entry of combustion chamber place.So far, especially in pumping stages model, this situation is not taken into full account for gas engine.Especially therefore, gas engine (only noting the mixture pressure before cylinder wherein) common static state consider as from the present invention identify know can not meet guarantee maintain restriction combustion air ratio.Thus, the solution of the present invention is for being provided in compounding substances quantity sensor that is that reliability aspect is improved and that mate better for transient operation, especially providing virtual compounding substances quantity sensor for the mixture before compressor is formed.
The object relating to device utilizes the present invention to be realized by a kind of adjusting portion for gas internal-combustion engine according to claim 13.
The solution of the present invention also realizes this object in the device in view of a kind of gas internal-combustion engine according to claim 14.
Internal-combustion engine especially can have motor, and it has multiple cylinder and the gas handling system with fuel gas mixer and pumping stages.In addition receiver volume (it such as can be implemented with the form of bend pipe or mixing section etc.) being prepended to multiple cylinder in cylinder upstream turns out to be favourable.
In gas handling system, make gas internal-combustion engine be provided with plenum, be especially provided with the plenum comprising charge heat exchanger and especially turn out to be favourable.According to the size of gas internal-combustion engine, especially based on big-block engine, plenum can be single-stage or two-stage, be provided preferably with EGR portion.Especially bypass section to the pumping stages of gas handling system can be provided with in addition to walk around plenum.
As shown in the cyclic process simulation especially at gas engine place and test, the present invention especially runs the stability improving combustion air ratio in (carry-unload) at transient engine, thus can illustrate that larger load increases and also can coordinate load switchover operation more simply at test stand place on the other hand on the one hand.In addition, contribute to reaching current and emissions standards in the future according to the solution of the present invention applying virtual gas security.
These and other favourable improvement project of the present invention can be learnt by dependent claims and to be described in detail in the scope of improvement project and to realize the favourable possibility of the solution of the present invention when additional advantage is described.
In the scope of a particularly preferred improvement project, substantially guarantee to adjust air stream and/or gas flow at fuel gas mixer place according to input-mixture share in the scope determined in real time at the same time.Especially illustrate that one according to the compounding substances quantity sensor as virtual mixture quality Sensor Design, it is advantageously provided in the mixture quality stream in fuel gas mixer outlet port; This is favourable relative to mode so far.
Especially input-mixture the share of the air-gas mixture in the outlet port at fuel gas mixer and/or the output-mixture share at the cylinder of motor or the air-gas mixture at cylinder entrance or receiver place can be determined.
Particularly advantageously determine the input-mixture share of the air-gas mixture in the outlet port at fuel gas mixer, and/or determine the output-mixture share of the air-gas mixture in the cylinder of motor or cylinder ingress, especially at receiver place.Particularly advantageously, determine the state pressure before the cylinder of motor, preferably as the receiver pressure in receiver volume, and receiver volume is understood to and is prepended to cylinder in the upstream direction and the volume being placed on any type in plenum and/or bypass section on downstream direction.Such as, receiver volume can be the bend pipe of pumping stages or the volume of other structure space expansion section.Receiver volume is especially understood to the volume of the common volume exceeding pumping stages; Shown in the scope of improvement project, be preset in receiver pressure in receiver volume for reliably regulating gas internal-combustion engine particular importance, because the increase of the insecurity in the state of combustion gas mixt is associated with the increase of the size of receiver volume.To the adjustment of the receiver pressure in receiver volume therefore eliminate for pumping stages static state hypothesis in exist cannot the property weighed.
Preferably, the determination of mixture share comprises especially by means of for the parts of throttle mechanism and/or pumping stages and/or the flow equation determination mixture quality stream of volume determined.Especially make the input at fuel gas mixer place-mixture share with mixture quality stream and/or output-mixture share is associated with mixture quality stream.Especially can determine the mixture quality stream at restriction place, wherein, determine the flow of backflow and/or supercharging stream.Preferably, this can realize by means of the frictionless of the combustion gas in the desirable or reality of hypothesis or when having the flowing of friction at the flow equation of the compressible medium at the nozzle place of desirable or reality.
Preferably, the determination of mixture share additionally or alternatively comprise mixture state determination, especially at least for the temperature of mixture share and/or the determination of state pressure of the volume of pumping stages.Preferably, this thermodynamic equation of state by means of reality or desirable combustion gas realizes.
Consider state pressure in pumping stages, such as in large volume or turn out to be favourable as the pressure loss by throttling.Its final controlling element can arrange for affect such as at throttle place, the state pressure at throttle valve or other throttle mechanism place.At this, the throttle mechanism of pumping stages is regarded as arbitrarily for reducing pressure or the usual device regulating pressure, and except engine's throttling portion, compressor restriction also can belong to this if desired.Especially can be valve, valve or restriction as engine's throttling portion or also have the variable turbine geometrical construction of compressor.At this, restriction open completely and adjustment angle [alpha] between the position closed completely be normally used for describing the throttle position of such throttle mechanism; Multiple throttle mechanisms of the above-mentioned type also can with multiple or apply in phase independently of one another or mutually with the combination of different throttle mechanism.
Especially can be provided with engine's throttling portion in upstream and/or be provided with compressor restriction before receiver volume in bypass section.Especially can carry out the throttling of pumping stages according to the theory-of pumping stages and/or virtual condition pressure, be particularly useful for the throttling in motor and/or bypass section.
In a particularly preferred form of implementation, the improvement project pumping stages be arranged to that is between fuel gas mixer and motor is divided into multiple, especially at least two volumes, preferably just two large volumes.
The program turns out to be suitable, and wherein, what especially use in following steps is one or more:
-fill and purging method (especially when using the pressure and temperature information etc. of already present measuring point),
-in engine controller, calculate in real time mixture quality stream at the different parts place of pumping stages,
-same mixer is mixed into by gas meavuremeut unit, and it causes empty quasi-definite with the mixture quality of the combustion air ratio expected.
Input-mixture share is advantageously made to be associated with combustion air ratio, especially its theoretical value (LAMBDA_SOLL), wherein, the gas meavuremeut unit of fuel gas mixer instructs by means of stoichiometric air requirements (L_st) and/or combustion air ratio.This measure confirms to be suitable for controlling fuel gas mixer.
For multiple theory calculate volume of pumping stages and/or the determination of mixture share, especially mixture quality stream and/or mixture state that especially can realize intermediateness for the multiple actual housing volume of pumping stages in the volume of pumping stages, wherein, in pumping stages, the quantity of the intermediateness of mixture share is associated with the quantity of at least one large volume of pumping stages.Thus, pumping stages model can especially close to designing practically.
Preferably, state pressure is determined virtually, especially in analog and/or with calculating according to the computation model of pumping stages (it at least comprises the calculating volume of charge heat exchanger and/or receiver volume).In the scope of a particularly preferred improvement project, state pressure is determined as the receiver pressure in the receiver volume before the cylinder (its cylinder be prepended on the direction of upstream is then placed at plenum on the direction in downstream and/or bypass section) of motor.Charge heat exchanger volume is understood to the volume having temperature exchange of any type in principle; That this especially can comprise motor supply section of air inlet system and/or the volume of pumping stages.Above-mentioned volume turns out to be relevant especially to the description of pumping stages.
Preferably, multiple large volumes of pumping stages comprise one or more piece volumes of pumping stages, it is selected from: at least one, preferably two receiver volumes, especially at least one the cylinder volume in cluster engine (Motorblock), at least one charge heat exchanger volume, at least one compressor volume.
Further preferably, at least one large volume multiple of pumping stages comprise one or more piece volumes of pumping stages, and it is also selected from: especially at least one compressor bypass volume at bypass tube section and/or compressor bypass valve place; Especially at least one pumping stages volume at pumping tube section and/or motor and/or input throttle place.
Preferably, combustion gas operation is the combustion gas operation of spark ignition; It turns out to be especially efficiently and can be used as many application and realizes suitably.But in principle, other ignition principle, such as diesel oil or other liquid fuel igniting ignition system also applicable.Combustion gas run especially also can be alternatively have air-gas mixture external mix thing formed igniting beam run and when use diesel ignition beam or other liquid fuel igniting beam.
Usually, even if do not illustrate in previous section at this, also because more constant fuel mass, same exist to run with combustion gas or with liquid fuel, possibility as the combustion gas operating gas internal-combustion engine of diesel oil or liquefaction.Be in operation and so fuel mixture (comprising charge mixture and/or liquid fuel) flowed to motor.At this, motor can run (utilizing diesel oil or other liquid fuel) with diesel oil in a first operational state and run using combustion gas operation (utilizing the combustion gas as fuel in pressurized mixture) in the second running state.The gas internal-combustion engine of the type is also referred to as multi-fuel internal combustion engine (bi-fuel internal combustion engine) and can also runs by other the most different fuel except the preferred fuel of diesel oil and combustion gas is selected.Alternatively especially in combustion gas runs, gas internal-combustion engine can run with the formation of the external mix thing of gas-air mixture and diesel ignition beam in igniting beam runs.So, the motor of gas internal-combustion engine is also referred to as igniting beam motor and usually builds based on diesel engine structure and belong to state-of-the-art technology, especially in the scope of the application possibility of the environmental protection of big-block engine.Igniting beam motor also can utilize liquid fuel, as diesel oil or other liquefied fuel, as LNG Liquefied natural gas (LNG) or also have liquefied petroleum gas (LPG) (LPG) to run; Gas internal-combustion engine can have combustion gas diesel engine mostly for forming combustion gas-diesel engine.
Gas internal-combustion engine especially has ejecting system, and it preferably can electrical adjustment.Internal-combustion engine especially can have ejecting system in addition to this, and it is advantageously configured to common-rail injection system.Ejecting system especially can regulate for different combustion gas qualities, as biogas in liquid form or rock gas, or is also suitable for oil if plant wet goods is as liquid fuel.At this, but unit fuel injector-ejecting system that especially common-rail injection system has electrical adjustment if desired in addition turns out to be applicable.In combustion gas runs, ignition media can be added to the vaporized fuel of the reality of charge mixture in the cylinder or also be added in gas-entered passageway when high compression.In combustion gas runs, the combustion gas of especially spark ignition run in or igniting beam run in utilize the gas engine of external mix thing formation work generally in fuel applications more flexibly and discharge is lower.
Accompanying drawing explanation
Next compared with the prior art equally partly illustrated, embodiments of the invention are described with reference to the accompanying drawings now.It not necessarily should be shown to scale these embodiments, but accompanying drawing in order to set forth with schematically and/or the form of distortion slightly implement.To the instruction that can directly identify from accompanying drawing supplementary in, with reference to relevant prior art.To considering at this, when not departing from general thoughts of the present invention, can multiple remodeling and change be carried out in the form and details of form of implementation.In the description, in the accompanying drawings and in the claims disclosed feature of the present invention can individually but also can be not only important for improvement of the present invention with combination in any.In addition, all assembly drops be made up of at least two in feature disclosed in specification, accompanying drawing and/or claim within the scope of this invention.General thoughts of the present invention is not limited to precise forms that is shown below and illustrated preferred form of implementation or details, is also not limited to limited object compared with object required for protection in the claims.In illustrated dimensional range, the value be positioned within the described limit should can be used as limiting value and is disclosed and can applies arbitrarily and can be claimed.From the ensuing explanation of preferred embodiment and obtain additional advantage of the present invention, characteristic sum details with reference to the accompanying drawings; Wherein:
Fig. 1 shows the sketch of gas internal-combustion engine, its have fuel gas mixer and with the pumping stages of the plenum be made up of turbosupercharger and charge heat exchanger and after receiver volume with the motor of multiple cylinder, wherein, walk around plenum by bypass section, the combustion gas that gas internal-combustion engine is designed for spark ignition runs;
In the alternative shown with dotted line, gas internal-combustion engine also can be designed to combustion gas-diesel engine and run with pure diesel oil and with mixed running or with pure combustion gas run (such as when injection using when ignition mixture of diesel oil form as the operation of igniting beam) can run, wherein, the form of the common rail system that ejecting system is shown in broken lines is formed;
Fig. 2 shows the flow chart of the preferred form of implementation of the method for the input be associated with the mixture state before-mixture share determining air-gas mixture in the scope for determining in real time at the same time by means of the output be associated with the mixture state afterwards-mixture share of air-gas mixture, wherein, determine the input-mixture share of the air-gas mixture at fuel gas mixer place and adjust air stream and/or gas flow at fuel gas mixer place according to input-mixture share
Fig. 3 shows the schematic diagram of the preferred form of implementation of the controller structure run for double fuel, wherein, in pumping stages, determined the input-mixture share of the air-gas mixture of fuel gas mixer by the output-mixture share of the air-gas mixture being fed to motor by multiple intermediatenesses of mixture share by means of pumping stages model.
Embodiment
Fig. 1 shows gas internal-combustion engine 100, and it has the gas handling system of motor 10 and the pumping stages 30 with branch.In pumping stages, be especially furnished with fuel gas mixer 40 and (in order to form plenum) turbosupercharger 50 and at this with the charge heat exchanger 60 of the form of charger-air cooler and bypass 70.
At this, motor implements 16 cylinders as V-type motor, and it has 8 cylinder Ai on A side, i=1...8 and 8 cylinder Bi on B side, i=1...8; At this, cylinder arrangement and the quantity of the type only illustrate.The engine design with the cylinder of 10,12,20,24 or 28 cylinders or other quantity is also especially suitable for big-block engine and uses.
When as the alternative of bi-fuel internal combustion engine or additional design, internal-combustion engine also has the ejecting system 20 of dotted line display, it is formed as the common rail system with common rail 21 at this, from wherein branching out each cylinder Ai of multiple injection line 22 (there is sparger 23 and the individual accumulator 24 being prepended to sparger respectively) to motor 10, Bi, i=1...8.Ejecting system 20 be configured to by the fuel of liquid state, as diesel oil or also have other liquefaction or the fuel of liquid state divide composition, so that diesel oil run in as liquid fuel or combustion gas or igniting beam run in as igniting beam respectively at cylinder Ai, the burner oil when work cycle of Bi starts; This carries out under very high jet pressure.Correspondingly, motor 10 also have in this variation for liquid fuel, this especially diesel fuel common-rail injection system 20 and with the plenum 50 of charge heat exchanger 60 and with the bypass 70 for walking around plenum 50 and charge heat exchanger 60.
The pith shown with solid line of this this form of implementation of External Reference, the fuel gas mixer 40 being attached to pumping stages 30 place in the end of the inlet side of gas handling system aspirates pressurized air LL and is mixed into wherein by combustion gas BG from environment.Also the charge mixture (below be also called for short " mixture G ") that can be described as combustion gas mixt in combustion gas runs using mass flow rate m (') _ G ((') " illustrate on quality m or other parameter as point for clarity in the drawings) utilize suction pressure p1 and roughly corresponding to the intake temperature T1 of ambient temperature under be fed to the compressor 51 of turbosupercharger 50 by compressor section 32 and be compressed on compression pressure p2 under compression temperature T2 there.Compressor 51 is driven by turbine 52 and is therewith positioned on common turbocharger axis 53; The turbine 52 of exhaust system 90 is driven by the waste gas AG leaving motor 10 in exhaust system 90 again.Be heated to due to compression the mixture G on compression temperature T2 mass flow m (') _ G is fed to the cooling section 31 of pumping stages 30 and is guided in charge heat exchanger 60 through cooler construction 61 there; Here to carry out the heat exchange with the cooling medium in cooler construction 61 in the heat exchanger volume 62 shown in symbol, thus cooling mixture G.Combustion gas mixt leaves the heat exchanger volume of V3 size for mixture G is delivered to motor 10 with cooled form under charge temperature T3 and charge pressure p3 on the direction of supercharging section 33.
In pumping stages model, the more usual status parameter by means of pressure and temperature illustrates the state of the mixture G before compressor 51, at this intake temperature T1 before compressor 51 and suction pressure p1, or be described in the status parameter p2 had after compressor 51 by means of suitable compressor model, the state under the compressor pressure p2 of the raising of T2 and the compressor temperature T2 of raising after compressor 51; This is such as according to such as obtaining for the equation of state of gas of the gas of desirable or reality.With being associated with lower component, such as bend pipe and/or collection section of heat exchanger 60 and receiver 80, according to the large volume particular importance of the solution of the present invention pumping stages 30, thus by the other space of itself and pumping stages in order to the modeling of other gaseous state is associated with the heat exchanger volume V3 in pumping stages model or receiver volume V5.Correspondingly, the combustion gas mixt G in heat exchanger volume V3 presents status parameter p3, T3, and this increases charge pressure due to cooling and volume and charge temperature p3, T3 reduce.
The state of the mixture G in bypass 70 is substantially same according to the status parameter p1 in the ingress of bypass 70, the status parameter p3 in T1 or outlet port, T3 determine or when being flowed back to by bypass 70 conversely; That is, bypass mixture G_BP in the bypass section 71 of bypass 70 depends on the position (at this adjustment angle [alpha] VBP according to compressor bypass valve) of the pressure condition of existence and compressor restriction 72, before bypass section 71 especially can be used for excessive mixture G to return and guides to compressor 51, so that it is flowed to the cylinder Ai of motor 10 by recompression ground again, for burning in Bi.
Will with state p3, before the gaseous mixture G of T3 is delivered to motor 10, according to the mass flow m be directed into by engine's throttling portion 82 in receiver volume 81 (') gaseous mixture G is directed in receiver 80 when (and according to the receiver volume V5 under receiver pressure p 5 and receiver temperature T5) changes pressure and temperature by _ DK.At this, respectively the B side of the first and second receiver volume 81.B, 81.A and motor 10 and A side are associated, that is its in upstream arrangement at cylinder Ai, at the first and second supercharging section 33.B of B side and A side before Bi, after 33.A and after heat exchanger volume 62.At this, the first and second engine's throttling valve 82.Bs of engine's throttling portion 82 by being associated with the first and second receiver volume 81.B, 81.A respectively, 82.A is formed, wherein, and the first and second engine's throttling valve 82.B, 82.A can adjust independently of one another; They are following common with engine's throttling portion 82 reference more simply.Receiver volume 81 can be regarded as the first and second receiver volume 81.A and 81.B and.In receiver volume 81, mixture G increases due to volume and in the volume V5 of receiver volume 81, occupies the gaseous state characterized by p5 and T5 according to the position alpha DK of engine's throttling valve 82.A, 82.B; This according to the position of engine's throttling valve 82.B and 82.A and B side or mass flowrate m (') _ DK, B or m (') _ DK, the A of A side relevant.
In this form of implementation, mainly as its by compressor 51, heat exchanger volume 62 and receiver volume 81 in the region that provides, the exactly relative boundary provided by engine's throttling portion 82 and compressor restriction 72 or compressor 51, determine gaseous mixture G by pi, Ti, i=1,2 or Vj, pj, Tj, j=3,5 states characterized
Below, based on the pumping stages model of the gas internal-combustion engine 100 shown in this, for the receiver pressure p 5 in receiver volume V5 in other words for the regulating parameter set up based on receiver pressure p 5 (the receiver pressure p 5 of such as actual receiver pressure p 5_IST or theoretical receiver pressure p 5_SOLL or simulation), in multiple volumes be associated of pumping stages 30, determined the input-mixture share of the air-gas mixture at fuel gas mixer 40 place by multiple intermediatenesses of mixture share.
Demonstrate, can realize along pumping stages under the prerequisite not necessarily at static conditions corresponding to the adjustment of combustion air than LAMBDA_SOLL or stoichiometric air ratio Lst at mass flow m (the mass flow m of _ G and pressurized air LL ') (' the) _ LL of fuel gas mixer 40 place combustion gas BG.Therefore, the scheme of this form of implementation in pumping stages model (as according to Fig. 1) in order to the volume of comprehensive pumping stages considers at least two large volumes, i.e. receiver volume 80 and charge heat exchanger volume 62.In the scope of pumping stages model, according to the principle of (known in principle) filling and purging method to pumping stages 30 modeling.Change of state in these volumes is regarded as approximate isothermal at this.This relative to thermal insulation consideration mode by be restricted to the conservation of mass simplifies system and in particular, simplify internal-combustion engine or its pumping stages real-time while calculate.But, also can use adiabatic or changeable consideration mode in principle when computing capability is enough or conduct heat targetedly, to simulate the change of state in pumping stages.
In addition as seen from Figure 3, in addition for setting up the special hypothesis of pumping stages can realize in the scope of additional model, if unavailable for the measured value set up accordingly of pumping stages 30 time, so especially true.Such as, this relates to additional model (the p2_T2 module of compressor, which depict compressor 51 activity and by temperature and pressure (G (pl, Tl) state and the state (G (p2, T2)) after the compressor of the mixture G before compressor) is described.This such as also relates to the additional model (mass flow _ VBP) for compressor bypass valve, and it describes the mass flow by compressor bypass valve in the scope of flow equation.
Be in operation, fuel mixture comprised charge mixture and flow to motor 10.At this, to utilize in pressurized mixture as the combustion gas of fuel to run motor.According to pumping stages model (as utilize regulator 200 in figure 3 structure as described in), (there is status parameter p5 by means of with mixture state afterwards, output-mixture the share of the air-gas mixture T5) be associated (mass flow m (') _ G, ZYL) determine that at least one (has status parameter p0 with mixture state before, input-mixture the share of the air-gas mixture T0) be associated (mass flow m (') _ G, SOLL).As for pumping stages 30, fuel gas mixer 40 and receiver 80 or by means of pumping stages model realization, this is determined to the basis of the computation model of the entrance of motor 10.
Scheme according to this form of implementation is arranged to, and determines output-mixture share (mass flow m (') _ G, the ZYL of the air-gas mixture at motor supply unit place (at this at receiver 80 place)).In the scope of this real-time calculating at the same time, (there is status parameter pi by multiple intermediatenesses of mixture share, Ti, i=5,3,2,1) by output-mixture share (mass flow m (') _ G, ZYL) input-mixture share (mass flow m (') _ G, SOLL is determined).The quantity of intermediateness (there is status parameter pi, Ti, i=5,3,2,1) with in pumping stages volume (Vi, i=5,3,2, l) or parts E1, the quantity of E2, E3, E4 and C3 and C5 is associated.Input-mixture the share of air-gas mixture is determined at fuel gas mixer 40 place and according to the input-mixture share air stream of adjustment at fuel gas mixer 40 place and/or gas flow BG.
At this, in pumping stages model, multiple large volume is associated with pumping stages, it comprises: two receiver volume 81.B, 81.A (has the volume V5 that is associated and has the status parameter p5 of charge mixture wherein, T5), at least one cylinder volume in cluster engine, at least one charge heat exchanger volume 62 (has the volume V3 that is associated and has the status parameter p3 of charge mixture wherein, T3), (at least one compressor volume at compressor 51 place there is value V2 and there is the status parameter p2 of the charge mixture in its outlet port, T2) state or before compressor 51 (has the status parameter p1 of charge mixture, and there is the status parameter p0 of the environment (air) of withdrawing air T1), T0), as this is shown in Figure 1.
The parts E1 of gas handling system shown in Figure 1 is equally considered, E2, E3, E4 and C3 and C5 and simulation or calculate state or the mass flow of charge mixture thus in current pumping stages model.At this, this is only selected from other possible example a series of as preferred example; Such as, when two-stage supercharging, the pumping stages model of modification yet can consider other parts.In principle, in pumping stages model, also other volume can be considered.In limit case, pumping stages can be divided into limited little or infinitesimal sub-volume and to the determination of the state of charge mixture and mass flow so as especially poor-or the solution of Differential Systems obtain; The balance of this model refinement can be taked when considering the complexity calculating consumption and pumping stages to be simulated; Especially when considering real-time capacity.
To this, Fig. 2 is as the flow process of the preferred form of implementation of operation method flow chart principle shown for gas internal-combustion engine 100, it has fuel gas mixer 40, pumping stages 30 and with multiple cylinder Ai, Bi, the motor 10 being also referred to as gas engine at this of i=1..8, as this is according to Fig. 1.In principle, operation method in enforcement shown in figure 2 for realizing when the adjustment determination method for parameter at fuel gas mixer 40 place, can adjust Parameter adjustable whole air stream LL and/or gas flow BG by means of these.With reference to figure 2, the method is current arranges other step S1 to S9 in step so) based on pumping stages model shown here, and it is positioned the aforesaid parts E1 by the determined gas handling system of pumping stages model, E2, E3, E4 and C3 and C5 (it is correspondingly shown in Figure 1) place.
Particularly, the determination " backward " of the input-mixture share of parts E0 (being associated with fuel gas mixer 40 at this) realizes, that is by carrying out inverse from the output-mixture share of the known parts E4 in pumping stages.At this, parts E4 roughly corresponding to the cylinder Ai of motor 10 or motor 10, Bi, i=1..8.In the first step S1 of this defining method, utilize the corresponding special parameter being used for engine speed nMOT and receiver pressure p 5 and receiver temperature T5 to determine cylinder charge by the computing module in regulon R4, such as, the tolerance to the air consumption LAMBDA_a required at motor 10 place is described.Then, in the second step S2 of defining method, can the parts E4 place of gas handling system (at this such as to cylinder Ai, the cylinder entrance of Bi, i=1..8) preset mixture quality stream m (') _ G, ZYL.
Correspondingly, show the controller structure of regulator 200 in figure 3, it has the first regulon R4 in order to implementation step S1 and S2.Input parameter is engine speed nMOT, and cylinder incoming pressure (especially at this at receiver 80 or the receiver volume 81.B with total volume V5, the receiver pressure p 5 in 81.A) and the other gaseous state parameter be associated of mixture share in receiver 80 (there is receiver volume V5) if desired.
Then in the third step S3 of Fig. 2, as the other parts E1 of gas handling system, consider the receiver volume 81.B with the total volume V5 of receiver 80,81.A (being such as associated with the bend pipe be attached in pumping stages between cylinder entrance and engine's throttling valve DK or mixing section).
Above-mentioned known to receiver volume 81.A, pressure and temperature situation (receiver pressure p 5 in 81.BV5, receiver temperature T5) when, in the fourth step s 4 can by means of the regulon R5 shown in figure 3 determine by the mixture quality stream m of receiver (') _ RECEIVER.Regulon R5 has computing unit, it (that is has the receiver volume 81.B of volume V5 from the mixture state of the air-gas mixture receiver 80 (usually also referred to as receiving organ pipe), the status parameter p5 of charge mixture in 81.A, T5) utilize the equation of state of charge mixture and mass flow equation according to for receiving organ pipe 81.B, the filling of 81.A and purging method determination mixture quality stream m (') _ RECEIVER.
In addition, the preferred form of implementation of defining method in fig. 2 arranges charge heat exchanger 60 based on pumping stages model for another parts E2.In the volume V3 be associated of heat exchanger volume 62, charge mixture has a gaseous state, and it can be calculated by the charge pressure p3 of volume V3 and charge temperature T3 in the 5th step S5.Similarly, according to the defining method shown in this, determine by the mixture quality stream m of pressurizing heat exchanger 62 (') _ LLK.Corresponding to this, Fig. 3 show the charge heat exchanger 60 for determining the form by the charger-air cooler to have cooler construction 61 mass flow m (') the regulon R3 of _ LLK.This determine in the 6th step S6 by means of for the filling of volume V3 and purging method known mixture state in other words its thermodynamic (al) special parameter and corresponding mixture quality flow equation realize.
Then in the 7th step S7 can by means of mixture quality stream m (') _ G, ZYL, m (') _ RECEIVER and m (') _ LLK releases theoretical value LAMBDA-Soll and the stoichiometric air requirements (Lst) of combustion air ratio, that is releases the most important theories special parameter of the fuel at another parts E0 place of fuel gas mixer 40 in pumping stages 30.To this, the first adding element R45 and the second adding element R43 is set in controller structure shown in Figure 3, with determined by mixture quality flow equation mixture quality stream m (') _ G, SOLL; This realizes when considering for realizing the 7th step S7, namely for calculating another conditioner unit R0 than LAMBDA_SOLL and stoichiometric air requirements Lst of combustion air.
Then the suitable adjustment parameter in fuel gas mixer 40 place can be preset in the 8th step S8 thus, with the input-mixture share at fuel gas mixer 40 place according to present engine rotating speed nMOT and the adjustment of the pressure and temperature situation (roughly p5, T5) in cylinder ingress.
At this, pumping stages model design becomes to have two large volumes (i.e. receiver volume 81.B, 81.A (V5) and charge heat exchanger volume 62 (V3)) and combine at least for throttle valve 82 when considering the filling/purging method being used for two volumes, the corresponding flow equation of 72 and (there is status parameter p1 at the compressor model at compressor 51 place, T1 → p2, T2) be introduced into pumping stages 30 simulation or calculate in.This is enough at this problem that overcomes mentioned by beginning; Taken into full account in the pumping stages model of large volume (it is not taken into full account and therefore causes the combustion gas quality stream at fuel gas mixer place and take off coupling at the in esse combustion gas quality stream in motor place in hitherto known computational methods) defining method shown in figure 2.Demonstrate simultaneously, can relatively simply and implement efficiently computing time thus, so that available in the scope determined in real time at the same time with the defining method of the form shown in this.So can actual in real time fuel gas mixer 40 be adjusted in the current demand of motor 10.
In the improvement project of the defining method in fig. 2, Fig. 3 show in more detail regulon R3 and mass flow m (') _ DK, m (') _ RECEIVER and m (') feedback of _ LLK.This is meaningful for the situation being provided with bypass 70.According to Fig. 3, as the status parameter other input parameter of adjustment unit R 3 being considered to the charge mixture G of the mixture state after compressor 51, namely except mixture state in charge heat exchanger 60 or afterwards as compression pressure p2 and compression temperature T2, as charge pressure p3 and charge temperature T3.Obtain in the scope of another regulon R2 for describing compressor 51 of the mixture state (status parameter p2, T2) after compressor 51 in compressor model.
In pumping stages model, compressor 51 is considered another pumping stages device E3 with regulon R2 associated with it.The mixture quality stream m of charger-air cooler 60 (') _ LLK is used as the entrance of regulon.Its again with compressor bypass valve 72 place mixture quality stream m (') _ VBP and at engine's throttling valve 82.A, the mixture quality stream at 82.B place is correlated with.At this, these mixture quality streams are cumulative in adder unit R42, be preset in the ingress conveying of heat exchanger 60 mixture quality stream m (') _ LLK.At engine's throttling valve 82.B, the mixture quality stream m at 82.A place (') _ DK obtains as the output of adding element R45 again, that is from cylinder entrance and receiver volume mixture quality stream m (') _ G, ZYL carry out inverse.
The mixture quality stream m that led back by throttle DK (') _ DK another input of feeding back to regulon R2 (that is impact is for adjusting the pumping stages device C5 of the backflow of charge mixture by compressor 70) obtained to adder unit R42 by the output feedack of adder unit R45 shown in broken lines in figure 3.
By the mixture quality stream of compressor 70 again at another pumping stages device C3, namely obtain in the scope of the flow equation at this compressor bypass valve 72 place.If engine's throttling valve DK place mixture quality stream m (') _ DK obtains primarily of the position alpha DK of the throttle as pumping stages device C5, then compressor mixture quality stream m (') _ VBP primarily of compressor restriction 72 position alpha VBP and when considering the pressure condition in the beginning of compressor 70 and end, namely at consideration p1, T1 (the charge mixture state that is before compressor 51) and p3, T3 (the charge mixture state that is before throttle DK), obtains.
So another regulon R1 not only obtains the position alpha VBP of compressor restriction 72 as input parameter but also obtains the gaseous state parameter p 3 in charge heat exchanger 60, T3 and the suction pressure p1 at least before compressor, T1, wherein, temperature T1 can roughly corresponding to ambient temperature T0.
As a result, the method for operating gas internal-combustion engine 100 improved is realized when using in figure 3 controller structure 200 of display in detail.

Claims (14)

1. for a method for operating gas internal-combustion engine (100),
Described gas internal-combustion engine has
-fuel gas mixer (40), pumping stages (30) and
-with the motor (10) of multiple cylinder, wherein, in the process
-fuel mixture is comprised charge mixture flow to described motor (10) and utilize the combustion gas in charge mixture as fuel to run described motor (10) in combustion gas runs, wherein
-by means of the input be associated with the mixture state before at least one-mixture share of air-gas mixture, determine the output be associated with the mixture state afterwards-mixture share of air-gas mixture, and wherein, this determines the pumping stages model realization on the basis by means of the computation model being used as described pumping stages (30)
It is characterized in that,
-determine the output-mixture share of the air-gas mixture at motor supply unit place,
-in multiple volumes be associated of described pumping stages (30) by multiple intermediatenesses of mixture share by exporting-mixture share determines input-mixture share, wherein
-determine the air-gas mixture at described fuel gas mixer (40) place input-mixture share and according to the input-mixture share air stream of adjustment at described fuel gas mixer (40) place and/or gas flow.
2. method according to claim 1, it is characterized in that, at the same time in the scope determined in real time of the operation of described motor in multiple volumes be associated of described pumping stages (30) by multiple intermediatenesses of mixture share by exporting-mixture share determines input-mixture share.
3. method according to claim 1 and 2, is characterized in that,
-determine the air-gas mixture in the outlet port at described fuel gas mixer (40) input-mixture share and/or
-output-mixture the share determining at cylinder (Ai, Bi) or the cylinder entrance of described motor (10) or the air-gas mixture at receiver (80) place.
4. according to method in any one of the preceding claims wherein, it is characterized in that, the determination of mixture share comprises:
-by means of the flow equation determination mixture quality stream of the volume for described pumping stages (30), wherein, mixture quality stream is associated with the input at described fuel gas mixer (40) place-mixture share and/or mixture quality stream at motor supply unit place is associated with output-mixture share;
And/or
The determination of-mixture state the thermodynamic equation of state at least comprised by means of the reality in the volume be associated or desirable combustion gas determines state pressure and/or the temperature of the mixture share of the volume be associated of described pumping stages (30).
5. according to method in any one of the preceding claims wherein, it is characterized in that, the theoretical value (Lambda_SOLL) of combustion air ratio, especially combustion air ratio is associated with input-mixture share, wherein, the gas meavuremeut unit of described fuel gas mixer (40) is instructed by means of stoichiometric air requirements (L_st) and/or combustion air ratio.
6. according to method in any one of the preceding claims wherein, it is characterized in that, in the volume be associated of described pumping stages (30), the multiple theory calculate volume of determination for described pumping stages (30) of mixture share, especially mixture quality stream and/or the mixture state of intermediateness and/or the multiple actual housing volume for described pumping stages (30) realize, wherein, in described pumping stages (30), the quantity of the intermediateness of mixture share is associated with at least one large volume of described pumping stages (30).
7. according to method in any one of the preceding claims wherein, it is characterized in that, multiple large volumes of described pumping stages (30) comprise one or more piece volumes of described pumping stages (30), and it is selected from:
-at least one, preferably two receiver volumes (V5, p5, T5),
-at least one cylinder volume in cluster engine,
-at least one charge heat exchanger volume (V3, p3, T3),
-at least one compressor volume (V2, p2, T2).
8. according to method in any one of the preceding claims wherein, it is characterized in that, state pressure is defined as the cylinder (Ai at described motor (10), Bi) the receiver pressure (p5) in the receiver volume (81) before, described receiver volume is prepended to described cylinder (Ai, Bi) and on the direction in downstream, is placed on plenum and/or bypass section on the direction of upstream.
9. according to method in any one of the preceding claims wherein, it is characterized in that, state pressure is determined according to the computation model of described pumping stages (30) virtually, especially in analog and/or with calculating, and it comprises at least one calculating volume of charge heat exchanger (60) and/or receiver volume (81).
10. according to method in any one of the preceding claims wherein, it is characterized in that, the number of at least one large volume of described pumping stages (30) comprises one or more piece volumes of described pumping stages (30), and it is also selected from:
-especially at least one compressor bypass volume (Vl, pl, Tl to V3, p3, T3) at bypass tube section and/or compressor bypass valve (72) place;
-especially at least one pumping stages volume at pumping tube section and/or motor-and/or input throttle (82) place.
11. according to method in any one of the preceding claims wherein, it is characterized in that, determine in restriction (72,82) the mixture quality stream at place, wherein, determines (the p3 that refluxes, T3, pl, Tl) and/or the flow of supercharging stream, the frictionless of the combustion gas of or reality desirable in hypothesis or when having the flowing of friction by means of the flow equation of the compressible medium at the nozzle place desirable or reality.
12., according to method in any one of the preceding claims wherein, is characterized in that, described combustion gas operation is that the combustion gas of spark ignition runs.
13. 1 kinds for gas internal-combustion engine (100), especially as the adjusting portion of the gas internal-combustion engine of spark ignition, it has
-fuel gas mixer (40), pumping stages (30) and
-with multiple cylinder, especially at the motor (10) of the receiver volume (81) of upstream arrangement before described cylinder,
The plenum of-described pumping stages (30), especially with charge heat exchanger, preferably with single-stage or two-stage supercharging portion, preferably with EGR, and
-be used for walking around described plenum with the bypass section of described pumping stages (30),
Wherein, described motor (10) can run using supplied comprising with the fuel mixture of combustion gas as the charge mixture of fuel in combustion gas runs, wherein
Described adjusting portion is configured to:
-by means of the output be associated with the mixture state afterwards-mixture share of the input be associated with the mixture state before at least one-mixture share determination air-gas mixture of air-gas mixture,
-input-mixture share of being determined in mixture state before by the output in mixture state afterwards-mixture share by means of the pumping stages model on basis of the computation model being used as described pumping stages (30),
It is characterized in that, described adjusting portion is configured in addition:
-determine the output-mixture share of the air-gas mixture at motor supply unit place, and
-in multiple volumes be associated of described pumping stages (30) by multiple intermediatenesses of mixture share by exporting-mixture state of mixture share determines input-mixture share, wherein
-determine the input-mixture share of the air-gas mixture at described fuel gas mixer (40) place and adjust air stream and/or gas flow at described fuel gas mixer (40) place according to input-mixture share.
14. 1 kinds of internal-combustion engines, it is configured to gas internal-combustion engine (100), is especially the gas internal-combustion engine of spark ignition, and it has
-fuel gas mixer (40), pumping stages (30) and
-with multiple cylinder, especially at the motor (10) of the receiver volume (81) of upstream arrangement before described cylinder,
The plenum of-described pumping stages (30), especially with charge heat exchanger, preferably with single-stage or two-stage supercharging portion, preferably with EGR, and
-be used for walking around described plenum with the bypass section of described pumping stages (30),
Wherein, described motor (10) can run using supplied comprising with the fuel mixture of combustion gas as the charge mixture of fuel in combustion gas runs, and
Have adjusting portion, it is configured to:
-by means of the output be associated with the mixture state afterwards-mixture share of the input be associated with the mixture state before at least one-mixture share determination air-gas mixture of air-gas mixture,
-input-mixture share of being determined in mixture state before by the output in mixture state afterwards-mixture share by means of the pumping stages model on basis of the computation model being used as described pumping stages (30),
It is characterized in that, described adjusting portion is configured in addition:
-determine the output-mixture share of the air-gas mixture at motor supply unit place, and
-in multiple volumes be associated of described pumping stages (30) by multiple intermediatenesses of mixture share by exporting-mixture state of mixture share determines input-mixture share, wherein
-determine the input-mixture share of the air-gas mixture at described fuel gas mixer (40) place and adjust air stream and/or gas flow at described fuel gas mixer (40) place according to input-mixture share.
CN201480019065.9A 2013-03-28 2014-01-20 Method and apparatus for running gas internal-combustion engine Active CN105324564B (en)

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CN105324564B (en) 2019-04-19
US9982633B2 (en) 2018-05-29
WO2014154314A1 (en) 2014-10-02
HK1221275A1 (en) 2017-05-26

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